CN106574641A - Hydraulic control device for operating machine - Google Patents

Hydraulic control device for operating machine Download PDF

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Publication number
CN106574641A
CN106574641A CN201580044422.1A CN201580044422A CN106574641A CN 106574641 A CN106574641 A CN 106574641A CN 201580044422 A CN201580044422 A CN 201580044422A CN 106574641 A CN106574641 A CN 106574641A
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CN
China
Prior art keywords
mentioned
hydraulic
cantilever
flow
hydraulic pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201580044422.1A
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Chinese (zh)
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CN106574641B (en
Inventor
森木秀
森木秀一
井村进也
宇田川勉
山下亮平
石川广二
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Hitachi Construction Machinery Co Ltd
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Hitachi Construction Machinery Co Ltd
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Publication of CN106574641A publication Critical patent/CN106574641A/en
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Publication of CN106574641B publication Critical patent/CN106574641B/en
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/30—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom
    • E02F3/32—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom working downwardly and towards the machine, e.g. with backhoes
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2271—Actuators and supports therefor and protection therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/10—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor in which the servomotor position is a function of the pressure also pressure regulators as operating means for such systems, the device itself may be a position indicating system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/0858—Arrangement of component parts installed on superstructures not otherwise provided for, e.g. electric components, fenders, air-conditioning units
    • E02F9/0883—Tanks, e.g. oil tank, urea tank, fuel tank
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate control

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

Provided is an energy-saving hydraulic control device for an operating machine, equipped with a specific actuator capable of supplying hydraulic fluid from a plurality of hydraulic fluid pumps. The hydraulic control device for an operating machine is provided with: a first pump and a second pump capable of communicating with a first hydraulic actuator; a first control valve capable of returning to a tank the hydraulic fluid discharged from the first hydraulic pump; and a load detection unit for detecting the load on the first hydraulic actuator, wherein the device is provided with a control valve drive unit that, in response to an increase in the load on the first hydraulic actuator, drives the first control valve so as to expand the communication area between the first hydraulic pump and the tank; and a flow rate control unit that, when hydraulic fluid is being supplied to the first hydraulic actuator by the first hydraulic pump and the second hydraulic pump, performs control to reduce the discharge flow rate of the first hydraulic pump, in response to an increase in the load on the first hydraulic actuator.

Description

The hydraulic control device of Work machine
Technical field
The present invention relates to the hydraulic control device of Work machine.
Background technology
The further increasing of particular drive that can be by the interflow of the pressure oil of two hydraulic pumps to drive with realization For the purpose of speed, with a kind of hydraulic control device of engineering machinery, which possesses：Electromotor；By engine-driven variable capacity First hydraulic pump and the second hydraulic pump of amount type；Can be by the pressure each discharged from these first hydraulic pumps and the second hydraulic pump The particular drive for collaborating to drive of power oil；Other different from particular drive driver；And by above-mentioned electromotor Drive and supply the 3rd hydraulic pump of the pressure oil being driven to above-mentioned other drivers, the hydraulic control of above-mentioned engineering machinery Device is characterised by, setting makes the pressure oil of above-mentioned 3rd hydraulic pump and above-mentioned first hydraulic pump and above-mentioned second hydraulic pump Pressure oil collaborates and can be selectively supplied to the converging valve of above-mentioned particular drive, and arranges the interflow to the converging valve The interflow cancel system released by function (for example, referring to patent documentation 1).
Prior art literature
Patent documentation
Patent documentation 1：Japanese Unexamined Patent Publication 2000-337307 publications
The content of the invention
Invent problem to be solved
According to the hydraulic control circuit of above-mentioned prior art, possesses the interflow released by the interflow function to converging valve Relief valve, when the load buckling of boom cylinder is high, makes interflow relief valve work, thus makes the discharge oil of the 3rd hydraulic pump from interflow Valve makes the discharge drops of the 3rd hydraulic pump to fuel tank circulation.Thus, the load of the 3rd hydraulic pump declines, by increasing capacitance it is possible to increase other The delivery flow of hydraulic pump, therefore, it is possible to guarantee the flow to the supply of the drivers such as the scraper bowl cylinder by other hydraulic pump drives, energy Good composition operation is realized enough.
However, in the case of the hydraulic control circuit of above-mentioned prior art, according to the viewpoint of energy-conservation, existing with after class Topic.
Usually, the leakage flow of hydraulic pump increases according to pressure is discharged, therefore discharges the higher, leakage flow of pressure to hydraulic pressure The impact of the total loss of pump is bigger.Therefore, if interflow relief valve work is made according to load pressure, and make the row of the 3rd hydraulic pump Go out drops, then can reduce pump and amount to leakage flow.However, not having and the 3rd liquid now in above-mentioned prior art The related description of the flow-control of press pump.
For example, in the case where known control completely is suitable for, the 3rd hydraulic pump is discharged corresponding to the operational ton of cantilever lever Flow, therefore not to driver supply, there is a possibility that return fuel tank invalid traffic increase.Thus produce the wave of energy Take.
The present invention is the scheme proposed based on above-mentioned thing, it is intended that can be from multiple hydraulic pumps possessing In the hydraulic control device of the Work machine of the specific driver of supply pressure oil, there is provided the hydraulic pressure of the Work machine of energy-saving Control device.
For solving the scheme of problem
To achieve these goals, the first invention is a kind of hydraulic control device of Work machine, is possessed：First hydraulic pressure drives Dynamic device；The first hydraulic pump that can be connected with above-mentioned first hydraulic unit driver and the second hydraulic pump；Above-mentioned first hydraulic pressure can be made First control valve of the pressure oil that pump is discharged to fuel tank circulation；And the load of above-mentioned first hydraulic unit driver is detected Load detecting portion, the hydraulic control device of above-mentioned Work machine are characterised by possessing：Control valve drive division, its reading are above-mentioned The detection signal that load detecting portion detects, and the increase of the load according to above-mentioned first hydraulic unit driver, so that above-mentioned first Hydraulic pump is driven to the above-mentioned first control valve with the mode of the connection area expansion of above-mentioned fuel tank；And flow-control portion, Which is read in the case of the oil from above-mentioned first hydraulic pump and above-mentioned second hydraulic pump to above-mentioned first hydraulic unit driver supply pressure Enter the detection signal that above-mentioned load detecting portion detects, and the increase of the load according to above-mentioned first hydraulic unit driver, dropped The control of the delivery flow of low above-mentioned first hydraulic pump.
The effect of invention
According to the present invention, as the load of the first hydraulic unit driver more increases, more reduces the delivery flow of the first hydraulic pump, The connection area for being driven to expand the first hydraulic pump and fuel tank to the first control valve, therefore the discharge pressure of the first hydraulic pump Drop, can reduce the leakage flow that pump amounts to.Thereby, it is possible to the invalid traffic for reducing from the first hydraulic pump discharging.As a result, energy The hydraulic control device of the Work machine of energy-saving is enough provided.
Description of the drawings
Fig. 1 is the Work machine of the first embodiment of the hydraulic control device for representing the Work machine for possessing the present invention Axonometric chart.
Fig. 2 is the hydraulic control circuit of the first embodiment of the hydraulic control device of the Work machine for representing the present invention Figure.
Fig. 3 is the knot of the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The schematic diagram of structure.
Fig. 4 is the mesh of the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The performance plot of one example of the chart of mark action operational part.
Fig. 5 is the company of the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The control block diagram of one example of the operation content of logical control unit.
Fig. 6 is the stream of the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The schematic diagram of the structure of amount control unit.
Fig. 7 is rising for the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The control block diagram of one example of the operation content of weighing arm flow partition operational part.
Fig. 8 is the outstanding of the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The control block diagram of one example of the operation content of arm target flow partition operational part.
Fig. 9 is the pump of the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The control block diagram of one example of the operation content of flow instruction operational part.
Figure 10 is the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The performance plot of one example of the chart of cantilever flow partition operational part.
Figure 11 is to controlling with the pump discharge in the first embodiment of the hydraulic control device of the Work machine of the present invention The performance plot that one example of the related action in portion is illustrated.
Figure 12 is the hydraulic control circuit of the second embodiment of the hydraulic control device of the Work machine for representing the present invention Figure.
Specific embodiment
Hereinafter, the embodiment of the hydraulic control device of the Work machine of the present invention is illustrated based on accompanying drawing.
Embodiment 1
Fig. 1 is the Work machine of the first embodiment of the hydraulic control device for representing the Work machine for possessing the present invention Axonometric chart, Fig. 2 are the hydraulic control circuit figures of the first embodiment of the hydraulic control device of the Work machine for representing the present invention.
As shown in figure 1, possessing the hydraulic excavating of the first embodiment of the hydraulic control device of the Work machine of the present invention Equipment is for lower traveling body 1, the upper rotation 2 being configured on the lower traveling body 1, with what is can rotated in the vertical direction Mode is connected to the front working rig of the upper rotation 2 and the electromotor 2A as prime mover.Front work tool is standby to be installed on The crane arm 3 of upper rotation 2, be installed on the crane arm 3 front end cantilever 4, and be installed on the cantilever 4 front end shovel Bucket 5.In addition, the front work tool standby a pair of crane arm cylinders 6 being driven to crane arm 3, the cantilever being driven to cantilever 4 Cylinder 7, and scraper bowl cylinder 8 that scraper bowl 5 is driven.
In addition, first action bars 9a, second operation of the hydraulic crawler excavator according to the driver's cabin for being arranged at upper rotation 1 The operation of bar 9b, the pressure oil that hydraulic pumping unit (not shown) is discharged are supplied to crane arm cylinder 6, boom cylinder via control valve 10 7th, scraper bowl cylinder 8 and rotary fluid motor 11.Crane arm cylinder 6, boom cylinder 7, each cylinder rod of scraper bowl cylinder 8 are stretched by pressure oil Contracting such that it is able to make position and the postural change of scraper bowl 5.In addition, rotary fluid motor 11 is rotated by pressure oil, so that Upper rotation 2 is turned round relative to lower traveling body 1.
Control valve 10 possesses the right use directional control valve 12a of traveling described later, travels left use directional control valve 12b, crane arm Used with first direction control valve 13a, crane arm second direction control valve 13b, cantilever first direction control valve 14b, cantilever Second direction control valve 14a, cantilever third direction control valve 14c, scraper bowl directional control valve 15a and revolution direction are controlled Valve 16c processed.
The speed probe 2Ax detected to engine speed is provided with electromotor 2A.It is provided with the bottom of in crane arm cylinder 6 The pressure transducer B6 detected by pressure transducer A6 that the pressure of side grease chamber is detected and the pressure to bar side grease chamber. In addition, boom cylinder 7 be provided with the pressure of bottom side grease chamber is detected as the load pressure transducer A7 of obtaining section and right The pressure transducer B7 detected by the pressure of bar side grease chamber.Equally, it is provided with scraper bowl cylinder 8 and the pressure of bottom side grease chamber is examined The pressure transducer B8 detected by the pressure transducer A8 of survey and the pressure to bar side grease chamber.In addition, rotary fluid motor 11 Possess pressure transducer A11, the B11 for being detected to the revolution pressure of left and right.These pressure transducers A6～A8, B6～ The engine speed that the pressure signal and speed probe 2Ax that B8, A11, B11 are detected is detected is input into controller described later 100。
As shown in Fig. 2 the pump installation 20 of the composition first embodiment of the hydraulic control device of the Work machine of the present invention Possess the first hydraulic pump 20a, the second hydraulic pump 20b and the 3rd hydraulic pump 20c of the hydraulic pump as variable capacity type.First ～the three hydraulic pump 20a～20c is driven by electromotor 2A.
First hydraulic pump 20a possesses the adjustor being driven by the command signal from controller described later 100 20d, the delivery flow of the pressure oil for being controlled is supplied to the first pump line line 21a.Equally, the second hydraulic pump 20b possesses and passes through The adjustor 20e that originally command signal of controller described later 100 is driven, the delivery flow of the pressure oil for being controlled is supplied To the second pump line line 21b.In addition, the 3rd hydraulic pump 20c possesses being carried out by the command signal from controller described later 100 The adjustor 20f of driving, the delivery flow of the pressure oil for being controlled is supplied to the 3rd pump line line 21c.
For the purpose of simplifying the description, omit be not directly dependent upon with present embodiment overflow valve, return loop, load check valve Deng.In addition, in the present embodiment, the example suitable for known standard-sized sheet commutation type hydraulic control device is illustrated, but The present invention is not limited to this.
The the first pump line line 21a connected in the outlet with the first hydraulic pump 20a is configured with traveling and right uses directional control valve 12a, scraper bowl directional control valve 15a, cantilever second direction controls valve 14a and crane arm first direction control valve 13a. It is configured to the series loop preferential to travel right use directional control valve 12a, remaining scraper bowl directional control valve 15a, cantilever are used Second direction controls valve 14a and crane arm first direction control valve 13a is configured to shunt circuit.
In the second pump line line 21b that the outlet with the second hydraulic pump 20b is connected, crane arm second direction control is configured with Valve 13b processed, cantilever first direction controls valve 14b and travels left to use directional control valve 12b.Crane arm second direction control Valve 13b and cantilever first direction control valve 14b are configured to shunt circuit, travel left directional control valve 12b and are configured to simultaneously Connection-series loop, but it is configured with the left shunt circuit with directional control valve 12b of traveling and only allow from the second hydraulic pump 20b The check-valves 17 and restriction 18 of side inflow.In addition, the left use directional control valve 12b of traveling can be with via traveling communicating valve 19 First hydraulic pump 20 is connected.
In the 3rd pump line line 21c that the outlet with the 3rd hydraulic pump 20c is connected, cantilever third direction control is configured with Directional control valve 16c is used in valve 14c and revolution.It is configured to turn round with directional control valve 16c preferential series loop.
Additionally, crane arm first direction controls the outlet port and crane arm second direction control valve 13b's of valve 13a Outlet port is connected with crane arm cylinder 6 via interflow path (not shown).In addition, cantilever controls valve 14a's with second direction Outlet port, cantilever first direction controls the outlet port that the outlet port and cantilever third direction of valve 14b controls valve Connect with boom cylinder 7 via interflow path (not shown).In addition, outlet port and scraper bowl of the scraper bowl with directional control valve 15a Cylinder 5 is connected, and the outlet port of revolution directional control valve 16c is connected with rotary fluid motor 11.
In Fig. 2, the first action bars 9a～the 4th action bars 9d internally possesses pilot valve (not shown) respectively, produce with it is each The corresponding elder generation's pilot of operational ton of the tilt rotation operation of action bars.First pilot from each action bars is supplied to all directions control The operating portion of valve processed.
It is connected to scraper bowl directional control valve 15a from the first action bars 9a by the pilot line that dotted line BkC and BkD are represented Operating portion, supplies the first pilot of scraper bowl loading and scraper bowl produced according to the operational ton of the tilt rotation of action bars operation and unloads first Pilot.In addition, crane arm first direction control is connected to from the first action bars 9a by the pilot line that dotted line BmD and BmU are represented Valve 13a processed and crane arm control each operating portion of valve 13b with second direction, supply the behaviour according to the operation of the tilt rotation of action bars The crane arm upward leader pressure measuring and produce, crane arm decline first pilot.
The pressure biography for loading that to scraper bowl pilot pressure is detected is provided with the pilot line represented by dotted line BkC and BkD Sensor 105 and the pressure transducer 106 detected by scraper bowl unloading pilot pressure.In addition, being represented by dotted line BmD and BmU Pilot line be provided with the pressure transducer 101 that detected to crane arm upward leader pressure and decline first pilot to crane arm The pressure transducer 102 detected by power.These pressure transducers 101,102,105 and 106 are that action indicates test section respectively, The pressure signal that these pressure transducers 101,102,105 and 106 are detected is input to controller 100.
Cantilever first direction control valve is connected to from the second action bars 9b by the pilot line that dotted line AmC and AmD are represented 14b, cantilever second direction controls valve 14a and cantilever third direction controls each operating portion of valve 14c, supplies according to operation The operational ton of the tilt rotation operation of bar and the cantilever that produces loads first pilot, the first pilot of cantilever unloading.In addition, by dotted line SwR The pilot line represented with SwL is connected to the operating portion of revolution directional control valve 16c from the second action bars 9b, supplies according to behaviour Make the tilt rotation operation of bar operational ton and produce the right first pilot of revolution, turn round left first pilot.
In the pilot line represented by dotted line AmC and AmD, the pressure biography for loading that to cantilever pilot pressure is detected is provided with Sensor 103 and the pressure transducer 104 detected by cantilever unloading pilot pressure.In addition, with cantilever third direction control The cantilever of the operating portion connection of valve 14c processed loads pilot line, is provided with the cantilever loading pilot pressure oil to being supplied and limits System or the cantilever 3 for disconnecting load air relief valve 22.
In addition, in the pilot line represented by dotted line SwR and SwL, being provided with to turning round the pressure detected by right pilot pressure Force transducer 108 and the pressure transducer 107 detected by the left pilot pressure of revolution.These pressure transducers 103,104, 107 and 108 is that action indicates test section, the pressure signal quilt that these pressure transducers 103,104,107 and 108 are detected respectively It is input into controller 100.
The pilot line represented by dotted line TrRF and TrRR is connected to from the 3rd lever apparatus 9c that traveling is right to use directional control valve The operating portion of 12a, supplies right first pilot, the traveling of advancing of traveling produced according to the operational ton of the tilt rotation of action bars operation It is right to retreat first pilot.
The pilot line represented by dotted line TrLF and TrLR is connected to from the 4th lever apparatus 9d that traveling is left to use directional control valve The operating portion of 12b, supply operational ton according to the operation of the tilt rotation of action bars and the traveling that produces it is left front enter first pilot, traveling It is left back to move back first pilot.
Hydraulic control device in present embodiment possesses controller 100.Controller 100 is from the revolution speed sensing shown in Fig. 1 Device 2Ax is input into engine speed, is input into the pilot pressure signal of each pilot line from above-mentioned pressure transducer 101～108.Separately Outward, the pressure signal of each driver is input into from the pressure transducer A6 shown in Fig. 1～A8, B6～B 8, A11, B11.
In addition, adjustor 20d from controller 100 to the first hydraulic pump 20a, the adjustor 20e of the second hydraulic pump 20b and The adjustor 20f difference output instruction signals of the 3rd hydraulic pump 20c, control to the delivery flow of each hydraulic pump 20a～20c System.In addition, controller 100 loads the operating portion output instruction signal of air relief valve 22, and the side to limit or disconnect to cantilever 3 Formula is controlled to the pressure that the cantilever that the operating portion supply of valve 14c is controlled to cantilever third direction loads pilot line Amc. If the command signal increases, the pilot pressure that the operating portion supply of valve 14c is controlled to cantilever third direction is disconnected.Its knot Really, the 3rd hydraulic pump 20c is disconnected with the connection of boom cylinder 7, and the pressure oil from the 3rd pump line line 21C is to fuel tank circulation.
Hereinafter, the control using accompanying drawing to the first embodiment of the hydraulic control device of the Work machine of the composition present invention Device is illustrated.Fig. 3 is the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention Structure schematic diagram, Fig. 4 be represent constitute the present invention Work machine hydraulic control device first embodiment control The performance plot of one example of the chart of the target action operational part of device processed, Fig. 5 are to represent the Work machine for constituting the present invention The control square of one example of the operation content of the connection control unit of the controller of the first embodiment of hydraulic control device Figure.
As shown in figure 3, controller 100 possesses：Computing is carried out to each target flow according to each first pilot and each load pressure Target action operational part 110；The command signal of the loading air relief valve 22 of cantilever 3 of the connected state of control control valve 10 is carried out The connection control unit 120 as connection control unit of computing；And each target flow for being calculated with target action operational part 110 and Each flow instruction signal based on the engine speed of speed probe 2Ax, to the first～tri- hydraulic pump 20a～20c Carry out the flow-control portion 130 as pump discharge control unit of computing.From flow-control portion 130 to the adjustor of each hydraulic pump 20d～20f output instruction signals, control the delivery flow of the first～tri- hydraulic pump 20a～20c respectively.
Target action operational part 110 increase respective target flow according to the increase of each pilot pressure of input, And the mode that respective target flow reduces is made according to the increase of each load pressure of input, each target flow is transported Calculate.In addition, carrying out following computing when interlocking operation：Compared with individually operated situation, each target flow tails off.
Illustrated using an example of the computing of Fig. 4 and mathematical expression to being carried out by target action operational part 110.In mesh Mark action operational part 110, carries out the figure of computing in each driver first pilot according to Fig. 4 that is stored with to standard flow Table.For example, turn round target flow Qsw to be returned according to the value of the maximum for selecting the right pilot pressure of revolution and the left pilot pressure of revolution Turn pilot pressure to calculate.Equally, cantilever loads standard flow Qamc0 and is calculated according to cantilever loading pilot pressure, unloads reference flow Amount Qamd0 unloads pilot pressure according to cantilever and calculates.
In addition, crane arm rises standard flow Qbmu0 being calculated according to crane arm upward leader pressure.Also, scraper bowl is loaded Standard flow Qbkc0 loads pilot pressure according to scraper bowl and calculates, and scraper bowl unloads standard flow Qbkd0 and unloads first pilot according to scraper bowl Power is calculated.
Target action operational part 110 calculates crane arm target flow according to revolution target flow Qsw and using arithmetic expression number 1 Qbm。
(mathematical expression 1)
Qbm=min (Qbm0,Qbm max-kswbm·Qsw) (1)
Here, Qbmmax is the higher limit of crane arm flow, compare maximal rate that crane arm rises to set.In addition, Kswbm is crane arm flow-reduction coefficient, and target flow Qsw more increases, target flow Qbm is less for crane arm for revolution.Additionally, Revolution target flow Qsw can be used more to increase, the less such chart of higher limit Qbmmax of crane arm flow, replace making With crane arm flow-reduction coefficient k swbm.
Target action operational part 110 is calculated rotary motive power Lsw respectively and is risen using arithmetic expression mathematical expression 2 and mathematical expression 3 Weighing arm power Lbm.
(mathematical expression 2)
Lsw=Psw·Qsw (2)
(mathematical expression 3)
Lbm=Pbmb·Qbm (3)
Here, Psw is revolution pressure, it is the left pressure of the revolution detected from pressure transducer A11 and B11 and turns round right pressure and select Value after the pressure of entrance side.In addition, Pbmb is crane arm base pressure, it is the bottom of the crane arm cylinder 6 that pressure transducer A6 is detected The pressure of side grease chamber.
Target action operational part 110 calculates scraper bowl power higher limit respectively using arithmetic expression mathematical expression 4 and mathematical expression 5 Lbkmax and cantilever power higher limit Lammax.
(mathematical expression 4)
Lbk max=kbk(Lmax-Lsw-Lbm) (4)
(mathematical expression 5)
Lam max=kam(Lmax-Lsw-Lbm) (5)
Here, Lmax is the vertical power higher limit of system.In addition, kbk represents the scraper bowl coefficient of impact, kam represents that cantilever is moved Force coefficient.Scraper bowl coefficient of impact kbk and cantilever coefficient of impact kam loads first pilot BkC, the first pilot of scraper bowl unloading using scraper bowl BkD, cantilever load first pilot AmC, first pilot AmD of cantilever unloading and arithmetic expression number 6 to calculate.
(mathematical expression 6)
kbk：kam=max (BkC, BkD)：Max (AmC, AmD) (6)
Target action operational part 110 loads standard flow Qbkc0, scraper bowl unloading standard flow Qbkd0, scraper bowl using scraper bowl Power upper limit Lbkmax and arithmetic expression number 7 are calculating scraper bowl target flow Qbk.In addition, target action operational part 110 is using outstanding Arm loads standard flow Qamc0, cantilever unloading standard flow Qamd0, cantilever power upper limit Lammax and arithmetic expression number 8 to calculate Go out cantilever target flow Qam.
(mathematical expression 7)
Qbk=min (Qbkc0, Qbkd0, Lbk max/Pbk) (7)
(mathematical expression 8)
Qam=min (Qamc0, Qamd0, Lam max/Pam) (8)
Here, Pbk is the pressure and bar side grease chamber of the bottom side grease chamber of the scraper bowl cylinder 8 detected from pressure transducer A8 and B8 Pressure select entrance side pressure after value.In addition, Pam is the bottom of the boom cylinder 7 detected from pressure transducer A7 and B7 The pressure of the pressure and bar side grease chamber of side grease chamber selects the value after the pressure of entrance side.
Hereinafter, an example of the computing using Fig. 5 to being carried out by connection control unit 120 is illustrated.Connection control unit 120 possess first function generator 120a and solenoid-driven instruction map portion 120b.
As shown in figure 5, the bottom side grease chamber of boom cylinder 7 that first function generator 120a input pressures sensors A 7 is detected Pressure.In first function generator 120a, cantilever 3 is stored in catalog in advance and load pilot pressure relative to boom cylinder 7 The limited characteristic of pressure of bottom side grease chamber be used as chart M1.Chart M1 becomes the pressure of the bottom side grease chamber of boom cylinder 7 and more increases Plus more make cantilever 3 load the characteristic that pilot pressure is reduced.The cantilever 3 calculated by first function generator 120a loads pilot pressure Limited characteristic signal output to solenoid-driven instruction map portion 120b.
Solenoid-driven instruction map portion 120b is input into the loading pilot pressure of cantilever 3 from first function generator 120a Limited characteristic signal, and calculate the command signal that corresponding with limited characteristic signal cantilever 3 loads air relief valve 22.It is concrete and Speech, if the command signal that cantilever 3 loads air relief valve 22 increases, controls the operating portion supply of valve 14c to cantilever with third direction Pilot pressure decline and disconnect, therefore possess adjoint input signal increase and output signal increase characteristic.By electromagnetic valve The command signal that driving instruction transformation component 120b is calculated exports to cantilever 3 operating portion for loading air relief valve 22.
Therefore, the pressure of the bottom side grease chamber of boom cylinder 7 more increases, and the operating portion of valve 14c is controlled with third direction to cantilever The pilot pressure of supply more declines.
Additionally, here, it is desirable to load the limited characteristic of pilot pressure according to cantilever 3 and start the cantilever of reduction from certain value Pump row of the pressure value of the bottom side grease chamber of cylinder 7 for the probability of the leakage loss with the friction loss more than hydraulic pump of hydraulic pump Go out more than pressure, set based on the loss property of hydraulic pump.
Hereinafter, the flow-control portion 130 as pump discharge control unit is illustrated using accompanying drawing.Fig. 6 is to represent composition The signal of the structure in the flow-control portion of the controller of the first embodiment of the hydraulic control device of the Work machine of the present invention Figure, Fig. 7 are the crane arms of the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The control block diagram of one example of the operation content of flow partition operational part, Fig. 8 are to represent the Work machine for constituting the present invention One of operation content of cantilever target flow partition operational part of controller of first embodiment of hydraulic control device The control block diagram of example, Fig. 9 are the first embodiments of the hydraulic control device for representing the Work machine for constituting the present invention The control block diagram of one example of the operation content in the pump discharge ordering calculation portion of controller.In Fig. 6 to Fig. 9, with Fig. 1 extremely Symbol identical symbol shown in Fig. 5 is a same part, therefore omits detail explanation.
Shown, flow-control portion 130 possesses：The target flow of each of the multiple directions control valve of crane arm 3 is carried out The crane arm flow partition operational part 131 of partition computing；The target flow of each of the multiple directions control valve of cantilever 4 is carried out The cantilever flow partition operational part 132 of partition computing；And calculating each pump based on each target flow that partition is calculated Flow, and to the adjustor 20d～20f output instruction signals of each hydraulic pump, so as to the first～tri- hydraulic pump 20a～20c The pump discharge ordering calculation portion 133 that is controlled of delivery flow.
Illustrated using an example of computings of the Fig. 7 to being carried out by crane arm flow partition operational part 131.Crane arm Flow partition operational part 131 possesses first function generator 131a, minima selector 131b, subtracts calculation device 131c, second function Generator 131d, the 3rd function generator of more vairable 131e and the 4th function generator of more vairable 131f.
First function generator 131a is input into the crane arm target flow from target action operational part 110.In the first letter Number producer 131a, is used as relative to the 2 guiding valve target flow of crane arm of crane arm target flow in catalog storage in advance Chart M3a.Chart M3a becomes the characteristic that crane arm target flow more increases, more makes the increase of 2 guiding valve target flow of crane arm. This, for example, it is also possible to by 2 guiding valve target flow rate of crane arm for crane arm target flow half.In this case, as long as not It is related to restriction described later, then 1 guiding valve target flow of crane arm and 2 guiding valve target flow of crane arm are respectively crane arm target flow Half.The 2 guiding valve target flow signal of crane arm for calculating is output to minima selector 131b.
Minima selector 131b be input into from first function generator 131a 2 guiding valve target flow signal of crane arm, Signal from second function generator 131d described later, the restriction signal from the 3rd function generator of more vairable 131e and from The restriction signal of four function generator of more vairable 131f, carries out computing, and slides its minima as crane arm 2 to the minima in them Valve target flow and export to subtracting and calculate device 131c and pump discharge ordering calculation portion 133.
Subtract calculation device 131c to be input into from the crane arm target flow of target action operational part 110 and from minima selector The 2 guiding valve target flow of crane arm of 131b, and 2 guiding valve target flow of crane arm is carried out subtracting calculation according to crane arm target flow, Thus computing is carried out to 1 guiding valve target flow of crane arm.By the 1 guiding valve target flow signal output of crane arm for calculating to pump discharge Ordering calculation portion 133.
The crane arm upward leader pressure that second function generator 131d input pressures sensor 101 is detected, and will limit Signal output processed is to minima selector 131b.In second function generator 131d, 2 guiding valve of crane arm is stored in original table in advance Target flow is used as chart M3b relative to the higher limit of crane arm upward leader pressure.Chart M3b and crane arm second direction The entrance side open nature of control valve 13b is generally proportionate, correspondingly increases with crane arm upward leader pressure.That is, with crane arm The opening that valve 13c is controlled with second direction correspondingly increases the higher limit of 2 guiding valve target flow of crane arm.
Cantilever that 3rd function generator of more vairable 131e input pressures sensor 103 is detected loads pilot pressure, will be from advance The signal output that the chart M3c being stored in catalog is obtained is to minima selector 131b.Here, chart M3c is used with cantilever First direction control valve 14b is generally proportionate relative to the entrance side open nature that cantilever loads pilot pressure, loads with cantilever Pilot pressure correspondingly reduces the upper limit of 2 guiding valve target flow of crane arm.
Cantilever that 4th function generator of more vairable 131f input pressures sensor 104 is detected unloading pilot pressure, will be from advance The signal output that the chart M3d being stored in catalog is obtained is to minima selector 131b.Here, chart M3d is used with cantilever First direction control valve 14b is generally proportionate relative to the entrance side open nature that cantilever unloads pilot pressure, unloads with cantilever Pilot pressure correspondingly reduces the higher limit of 2 guiding valve target flow of crane arm.
In crane arm flow partition operational part 131, lifting is limited by these 2 guiding valve target flow higher limits of crane arm 2 guiding valve target flow of arm, deducts 2 guiding valve target flow of crane arm from crane arm target flow, calculates 1 guiding valve target stream of crane arm Amount.
Then, an example of the computing using Fig. 8 to being carried out by cantilever flow partition operational part 132 is illustrated.It is outstanding Arm flow partition operational part 132 possesses first function generator 132a, the first minima selector 132b, first subtracts calculation device 132c, second function generator 132d, the 3rd function generator of more vairable 132e, the first maximum selection rule portion 132f, the 4th function are produced Device 132g, the second minima selector 132h, second subtract calculation device 132i, the 5th function generator of more vairable 132J, the 6th function generator of more vairable 132k, the second maximum selection rule portion 132L, the 7th function generator of more vairable 132m and the 8th function generator of more vairable 132n.
Cantilever of first function generator 132a and the 4th function generator of more vairable 132g inputs from target action operational part 110 Target flow.In first function generator 132a, the 2 guiding valve mesh of cantilever relative to table cantilever target flow is stored in guide look in advance Mark flow is used as chart M4a, in the 4th function generator of more vairable 132g, stores relative to cantilever target flow in catalog in advance 3 guiding valve target flow of cantilever is used as chart M4b.Chart M4a and M4b become cantilever target flow more increase, more make cantilever 2 and The characteristic that 3 guiding valve target flows increase.Here, for example, it is also possible to being cantilever target by cantilever 2 and 3 guiding valve target flow rates / 3rd of flow.In this case, as long as being not related to restriction described later, then 1 guiding valve target flow of cantilever, 2 guiding valve mesh of cantilever Mark flow, 3 guiding valve target flow of cantilever respectively become 1/3rd of cantilever target flow.The 2 guiding valve target stream of cantilever for calculating Amount signal is output to the first minima selector 132b.The 3 guiding valve target flow signal of cantilever for calculating is output to second most Little value selector 132h.
First minima selector 132b is input into the 2 guiding valve target flow signal of cantilever from first function generator 132a With the restriction signal from the first maximum selection rule portion 132f described later, computing is carried out to the minima in them, and by which most Little value is exported as 2 guiding valve target flow signal of cantilever to first and subtracts calculation device 132c and pump discharge ordering calculation portion 133.
First subtracts calculation device 132c is input into from the cantilever target flow of target action operational part 110 and from the first minima The 2 guiding valve target flow of cantilever of selector 132b, deducts 2 guiding valve target flow of cantilever from cantilever target flow, so as to cantilever 1 Guiding valve target flow reference signal carries out computing.The 1 guiding valve target flow reference signal of cantilever for calculating is exported to second and subtracts calculation Device 132i.
Cantilever that second function generator 132d input pressures sensor 103 is detected loads pilot pressure, will be from advance The signal output that the chart M4c being stored in catalog is obtained is to the first maximum selection rule portion 132f.Here, chart M4c with it is outstanding It is generally proportionate relative to the entrance side open nature that cantilever loads pilot pressure that arm second direction controls valve 14a, and with it is outstanding Arm loads pilot pressure and correspondingly increases 2 guiding valve target flow higher limit of cantilever.
Cantilever that 3rd function generator of more vairable 132e input pressures sensor 104 is detected unloading pilot pressure, will be from advance The signal output that the chart M4d being stored in catalog is obtained is to the first maximum selection rule portion 132f.Here, chart M4d with it is outstanding It is generally proportionate relative to the entrance side open nature that cantilever unloads pilot pressure that arm second direction controls valve 14a, and with it is outstanding Arm unloading pilot pressure correspondingly increases 2 guiding valve target flow higher limit of cantilever.
The output of the first maximum selection rule portion 132f input second function generator 132d and the 3rd function generator of more vairable 132e Output, computing is carried out to the maximum in them, and its maximum is exported to the first minima selector 132b.
Second minima selector 132h is input into 3 guiding valve target flow of the cantilever letter from the 4th function generator of more vairable 132g Number, the restriction signal from the second maximum selection rule portion 132L described later and from the 7th function generator of more vairable 132m and the 8th The restriction signal of function generator of more vairable 132n, carries out computing to the minima in them, and using its minima as 3 guiding valve mesh of cantilever Mark flow signal and export to second and subtract calculation device 132i and pump discharge ordering calculation portion 133.
Second subtract calculate device 132i input first subtract calculate 1 guiding valve target flow reference signal of cantilever that device 132c calculates and from The 3 guiding valve target flow of cantilever of the second minima selector 132h, deducts cantilever 3 from 1 guiding valve target flow reference signal of cantilever Guiding valve target flow, thus carries out computing to 1 guiding valve target flow reference signal of cantilever.The 1 guiding valve target flow of cantilever for calculating Signal output is to pump discharge ordering calculation portion 133.
Cantilever that 5th function generator of more vairable 132J input pressures sensor 103 is detected loads pilot pressure, will be from advance The signal output that the chart M4f being stored in catalog is obtained is to the second maximum selection rule portion 132L.Here, chart M4f with it is outstanding It is generally proportionate relative to the entrance side open nature that cantilever loads pilot pressure that arm third direction controls valve 14c, and with it is outstanding Arm loads pilot pressure and correspondingly increases 3 guiding valve target flow higher limit of cantilever.Additionally, the characteristic of chart M4f is with chart M4c's Characteristic is compared, will export elevated input value (cantilever loading pilot pressure) be set to it is higher.Thus, the of operation cantilever 4 When the operational ton of two action bars 9b is few, the signal of 2 guiding valve target flow of cantilever is first generated, in the second action bars of operation cantilever 4 After the operational ton of 9b increases, the signal of 3 guiding valve target flow of cantilever is regenerated.
Cantilever that 6th function generator of more vairable 132k input pressures sensor 104 is detected unloading pilot pressure, will be from advance The signal output that the chart M4g being stored in catalog is obtained is to the second maximum selection rule portion 132L.Here, chart M4g with it is outstanding It is generally proportionate relative to the entrance side open nature that cantilever unloads pilot pressure that arm third direction controls valve 14c, and with it is outstanding Arm unloading pilot pressure correspondingly increases 3 guiding valve target flow higher limit of cantilever.Additionally, the characteristic of chart M4g is with chart M4d's Characteristic is compared, will export elevated input value (cantilever unloading pilot pressure) be set to it is higher.Thus, the of operation cantilever 4 The signal of 2 guiding valve target flow of cantilever when the operational ton of two action bars 9b is few, is first generated, is increased in the operational ton of the second action bars 9b In addition after, regenerate the signal of 3 guiding valve target flow of cantilever.
Second maximum selection rule portion 132L is input into the output of the 5th function generator of more vairable 132J and the 6th function generator of more vairable 132k Output, computing is carried out to the maximum in them, and its maximum is exported to the second minima selector 132h.
The pressure of the bottom side grease chamber of the boom cylinder 7 that the 7th function generator of more vairable 132m input pressures sensors A 7 is detected, will The signal output obtained from the chart M4i being stored in advance in catalog is to the second minima selector 132h.Here, for figure The setting of table M4i in describing hereinafter, but will correspondingly make 3 guiding valve target flow of cantilever with the pressure of the bottom side grease chamber of boom cylinder 7 Higher limit is reduced.
The right pilot pressure of revolution and revolution that 8th function generator of more vairable 132b input pressures sensor 107 and 108 is detected Maximum in left pilot pressure is used as turning round pilot pressure, by what is obtained from the chart M4h being stored in advance in catalog Signal output is to the second minima selector 132h.Here, chart M4h is first relative to revolution with directional control valve 16c with revolution The center bypass open nature of pilot power is generally proportionate, and correspondingly makes 3 guiding valve target flow of cantilever with revolution pilot pressure Higher limit is reduced.
In cantilever flow partition operational part 132, with calculated by target action operational part 110 cantilever target flow, cantilever Based on loading pilot pressure, cantilever unloading pilot pressure etc., 1～3 guiding valve target flow of cantilever is calculated, but as described above, As the chart M4f and the 3rd function of chart M4c and the 5th function generator of more vairable 132J in second function generator 132d are produced In the chart M4g of the chart M4d and the 6th function generator of more vairable 132k of raw device 132e, change the output elevated point relative to input, Therefore the increase of the operational ton of the second action bars 9b of attended operation cantilever 4, sequentially generates according to 1 guiding valve target flow of cantilever.
Then, the operational ton according to the second action bars 9b, generates 2 guiding valve target stream of 1 guiding valve target flow of cantilever and cantilever Amount, and when operational ton increases, generate 3 guiding valve target flow of cantilever.
Hereinafter, an example of the computing using Fig. 9 to being carried out by pump discharge ordering calculation portion 133 is illustrated.Pump stream Amount ordering calculation portion 133 possess the first maximum selection rule portion 133a, the first divider 133b, first function generator 133c, the Two maximum selection rule portion 133d, the second divider 133e, second function generator 133f, the 3rd maximum selection rule portion 133g, Three divider 133h and the 3rd function generator of more vairable 133i.
First maximum selection rule portion 133a be input into from target action operational part 110 scraper bowl target flow signal, from The 1 guiding valve target flow signal of crane arm of crane arm flow partition operational part 131 and from cantilever flow partition operational part 132 2 guiding valve target flow signal of cantilever, carries out computing to the maximum in them, and using its maximum as the first pump mesh Mark flow and export to the first divider 133b.
First divider 133b is input into the first pump target flow and revolution speed sensing from the first maximum selection rule portion 133a The engine speed that device 2Ax is detected, and with engine speed divided by the first pump target flow, thus to the first pump target instruction target word Carry out computing.By the first pump target instruction target word signal output for calculating to first function generator 133c.
First function generator 133c is input into the first pump target instruction target word signals for calculating of the first divider 133b, will be from advance The signal that the chart M5a being stored in catalog is obtained is exported to adjustor 20d as the first pump discharge command signal.By This, controls the delivery flow of the first hydraulic pump 20a.
Second maximum selection rule portion 133d is input into the 2 guiding valve target of crane arm from crane arm flow partition operational part 131 Flow signal and the 1 guiding valve target flow signal of cantilever from cantilever flow partition operational part 132, enter to the maximum in them Row computing, and its maximum is exported to the second divider 133e as the second pump target flow.
Second divider 133e is input into the second pump target flow and revolution speed sensing from the second maximum selection rule portion 133d The engine speed that device 2Ax is detected, and with engine speed divided by the second pump target flow, thus to the second pump target instruction target word Carry out computing.By the second pump target instruction target word signal output for calculating to second function generator 133f.
Second function generator 133f is input into the second pump target instruction target word signals for calculating of the second divider 133e, will be from advance The signal that the chart M5b being stored in catalog is obtained is exported to adjustor 20e as the second pump discharge command signal.Thus, Control the delivery flow of the second hydraulic pump 20b.
3rd maximum selection rule portion 133g be input into from target action operational part 110 revolution target flow signal and from The 3 guiding valve target flow signal of cantilever of cantilever flow partition operational part 132, carries out computing to the maximum in them, and by its Maximum is exported to the 3rd divider 133h as the 3rd pump target flow.
3rd divider 133h is input into the 3rd pump target flow and revolution speed sensing from the 3rd maximum selection rule portion 133g The engine speed that device 2Ax is detected, and with engine speed divided by the 3rd pump target flow, thus to the 3rd pump target instruction target word Carry out computing.The 3rd pump target instruction target word signal for calculating is exported to the 3rd function generator of more vairable 133i.
3rd function generator of more vairable 133i is input into the 3rd pump target instruction target word signals that calculate of the 3rd divider 133b, will be from advance The signal that the chart M5c being stored in catalog is obtained is exported to adjustor 20f as the 3rd pump discharge command signal.By This, controls the delivery flow of the 3rd hydraulic pump 20c.
In pump discharge ordering calculation portion 133,2 guiding valve target flow of cantilever is input into the first maximum selection rule portion 133a, 1 guiding valve target flow of cantilever is input into the second maximum selection rule portion 133d, is slided to the 3rd maximum selection rule portion 133g input cantilevers 3 Valve target flow, calculates the first pump target flow～the 3rd pump target flow respectively.Here, in cantilever flow partition operational part In 132, as described above, according to operation cantilever 4 the second action bars 9b operational ton increase, first generate 1 guiding valve mesh of cantilever Mark flow, then generates 2 guiding valve target flow of cantilever, ultimately produces 3 guiding valve target flow of cantilever.
Therefore, in the case where the second action bars 9b to operating cantilever 4 is operated, according to the increase of the operational ton, The second pump discharge command signal is initially produced, the first pump discharge command signal is then produced, the instruction of the 3rd pump discharge is finally produced Signal.
Additionally, in the present embodiment, to the situation for being set to 1 to the speed reducing ratio of each hydraulic pump from electromotor 2A is said It is bright.In the case of beyond speed reducing ratio is for 1, needs carry out computing corresponding with speed reducing ratio.
Then, the setting using Figure 10 to the chart of the 7th function generator of more vairable 132m of cantilever flow partition operational part 132 Illustrate.Figure 10 is the controller of the first embodiment of the hydraulic control device for representing the Work machine for constituting the present invention The performance plot of one example of the chart of cantilever flow partition operational part.
In Fig. 10, transverse axis represents the pressure of the bottom side grease chamber of boom cylinder 7, and the longitudinal axis represents 3 guiding valve target flow of cantilever Target flow.In addition, characteristic line A indicated by the solid line represents the first function generator 120a for being set in connection control unit 120 Chart M1 cantilever 3 load pilot pressure limited characteristic signal, the characteristic line B being represented by dashed line is to be set in the 7th function The chart M4i of generator 132m, represents the ceiling restriction of 3 guiding valve target flow of cantilever relative to the bottom side grease chamber of boom cylinder 7 The characteristic of pressure.
As shown in Figure 10, increases of the chart M4i (characteristic line B) with the pressure of the bottom side grease chamber of boom cylinder 7, reduces cantilever The higher limit of 3 guiding valve target flows, therefore the increase of the pressure of the bottom side grease chamber of adjoint boom cylinder 7, reduce cantilever 3 and load guide The chart M1 (characteristic line A) of the limited characteristic of pressure is identical with direction of action.But, the property settings of chart M4i (characteristic line B) , before the decline of characteristic line A is started (in the little region of the pressure of the bottom side grease chamber of boom cylinder 7), to start 3 guiding valve mesh of cantilever The reduction of the upper limit of mark flow.
Thus, in the case that the pressure in the bottom side grease chamber of boom cylinder 7 increased, 3 guiding valve target flow upper limit elder generation of cantilever Decline, therefore the delivery flow of the 3rd hydraulic pump 20c is reduced, then, the limited characteristic of pilot pressure is loaded according to cantilever 3, hanged Arm 3 load 22 action of air relief valve and cantilever third direction control valve 14c center bypass opening start to open at.Thus, cantilever 3 The guiding valve target flow upper limit declines, and the delivery flow of the 3rd hydraulic pump 20c is reduced, until cantilever controls valve 14c with third direction Center bypass opening open.As a result, can reduce controlling the bypass throttle damage that valve 14c is produced in cantilever third direction Lose.In addition, the entrance side flow to boom cylinder 7 that the center bypass of cantilever third direction control valve 14c is started to open at Change diminish, impact now can be reduced.
Hereinafter, the action using accompanying drawing to the first embodiment of the hydraulic control device of the Work machine of the present invention is carried out Explanation.Figure 11 be to the present invention Work machine hydraulic control device first embodiment in pump discharge control unit phase The performance plot that one example of the action of pass is illustrated.
In fig. 11, horizontal axis representing time, the longitudinal axis represent (a) pilot pressure, the discharge pressure of (b) hydraulic pump, (c) respectively Cantilever third direction control valve 14c centers bypass opening, (d) the 3rd hydraulic pump delivery flow, (e) the 4th hydraulic pump discharge stream Amount.In addition, the solid line in (b) represents the characteristic of the discharge pressure of the second hydraulic pump 20b, dotted line represents the 3rd hydraulic pump 20c's The characteristic of discharge pressure.In addition, moment T1 represents the moment for starting cantilever loading action, moment T2 represents that scraper bowl is connect with excavation surface Touch and wait and the moment of the pressure of the bottom side grease chamber of boom cylinder 7 increase, moment T3 represents that the pressure of the bottom side grease chamber of boom cylinder 7 enters one The moment that step increases.Additionally, for the simplification of explanation, omitting the action of the first hydraulic pump 20a illustrating.
First, if starting cantilever loading action from moment T1, such as shown in (a), cantilever loads pilot pressure and raises.And And, cantilever first direction controls valve 14b and the control valve 14c actions of cantilever third direction, and boom cylinder 7 is connected with each hydraulic pump It is logical, (b) shown in pump discharge pressure and be increased to pressure corresponding with the pressure of the bottom side grease chamber of boom cylinder 7.Now, in boom cylinder 7 Bottom side grease chamber pressure it is low in the case of, such as shown in (c), cantilever third direction controls the center bypass opening of valve 14c and closes Close.In addition, as shown in (d) and (e), the delivery flow of the delivery flow of the 3rd hydraulic pump 20c and the second hydraulic pump 20b increases, Cantilever 4 carries out action.
Then, in moment T2, for example, if scraper bowl 5 is contacted with excavation surface etc., the pressure of the bottom side grease chamber of boom cylinder 7 increases Plus, then as shown in (d), by flow-control portion 130, the delivery flow of the 3rd hydraulic pump 20c is reduced.Now, by cantilever stream Amount partition operational part 132, correspondingly significantly reduces the discharge stream of the 3rd hydraulic pump 20 with the pressure of the bottom side grease chamber of boom cylinder 7 Amount, therefore as shown in (e), the reduction amount of the delivery flow of the second hydraulic pump 20b diminishes, cantilever entrance side flow altogether is maintained In cantilever target flow.
Then, if the pressure of the bottom side grease chamber of boom cylinder 7 further increases, reach to connect control unit 120 in moment T3 Cantilever 3 load the pressure value that the limited characteristic of pilot pressure starts to reduce from certain value, then as shown in (c), cantilever is with the 3rd The center bypass opening of directional control valve 14c is started to open at, and as shown in (b), the discharge of the 3rd hydraulic pump 20c was pressed off under the beginning Drop.Additionally, the delivery flow of the 3rd moment T3 shown in (d) later hydraulic pump 20c is wished for standby flow.So, pass through The 3rd hydraulic pump 20c is made to operate with standby flow, so as to improve energy-saving effect.
In present embodiment, described standby flow refers to the pressure that must be flowed to protect the hydraulic pump for being operated The minimum delivery flow of power oil.
Usually, the leakage flow of hydraulic pump increases generally proportionately with discharge pressure, discharges and presses higher, leakage flow phase It is bigger for the impact of the loss of hydraulic pump.Therefore, in high capacity, compare by the 3rd hydraulic pump 20c and the second hydraulic pump 20b Both drives boom cylinder 7, as the hydraulic control device of present embodiment, only drives boom cylinder 7 by the second hydraulic pump 20b Pumping loss altogether can be reduced such that it is able to realize energy-conservation.
Further, since before the center bypass opening of cantilever third direction control valve 14c is started to open at, reducing the 3rd The delivery flow of hydraulic pump 20c, therefore, it is possible to reduce controlling the bypass throttle loss that valve 14c is produced in cantilever third direction. In addition, the entrance side flow to boom cylinder 7 for starting to open at of the center bypass opening of cantilever third direction control valve 14c Change diminishes, and can reduce impact now.
According to the first embodiment of the hydraulic control device of the Work machine of the above-mentioned present invention, the first hydraulic unit driver The load of (boom cylinder 7) more increases, more reduces the delivery flow of the first hydraulic pump (the 3rd hydraulic pump 20c), drives first to control Valve (cantilever with third direction control valve 14c) and expand the connection area of the first hydraulic pump and fuel tank, therefore reduce the first hydraulic pressure The discharge pressure of pump (the 3rd hydraulic pump 20c) such that it is able to reduce the leakage flow that pump amounts to.Thereby, it is possible to reduce from the first liquid The invalid traffic that press pump (the 3rd hydraulic pump 20c) is discharged.As a result, the hydraulic control dress of the Work machine of energy-saving can be provided Put.
In addition, the first embodiment of the hydraulic control device according to the Work machine of the above-mentioned present invention, due in root Expand the connected surface of the first hydraulic pump (the 3rd hydraulic pump 20c) and fuel tank according to the load of the first hydraulic unit driver (boom cylinder 7) Before product, the delivery flow of the first hydraulic pump (the 3rd hydraulic pump 20c) is reduced, therefore, it is possible to reduce controlling valve (cantilever first With third direction control valve 14c) produce bypass throttle loss.In addition, the first control valve (cantilever third direction control valve The change of the entrance side flow to the first hydraulic unit driver (boom cylinder 7) when 14c) being opened and closed diminishes, and can reduce rushing now Hit.
Embodiment 2
Hereinafter, the second embodiment of the hydraulic control device of the Work machine of the present invention is illustrated using accompanying drawing. Figure 12 is the hydraulic control circuit figure of the second embodiment of the hydraulic control device of the Work machine for representing the present invention.In Figure 12 In, same part is represented with the symbol identical symbol shown in Fig. 1 to Figure 11, omit detail explanation.
In the second embodiment of the hydraulic control device of the Work machine of the present invention, the structure of the system of entirety is substantially It is identical with first embodiment, but do not using controller 100, but hydraulic control device this point be only made up of hydraulic circuit It is different from first embodiment.
Specifically, as shown in figure 12, the adjustor 20f of the 3rd hydraulic pump 20c is by by the hydraulically powered auxiliary of guide Adjustor 20g is carrying out action.First pilot is supplied to auxiliary adjustor 20g via the first switching valve 23 from guide's hydraulic power source 25 Power oil.Correspondingly, adjustor 20f is to reduction the 3rd hydraulic pump of direction controlling for supply with from the pressure oil to auxiliary adjustor 20g The delivery flow of 20c.
First switching valve 23 is the pressure oil of the bottom side grease chamber to operating portion importing boom cylinder 7 and possesses spring in one side The switching valve that three port two position is put, has been linked with the oil circuit from guide's hydraulic power source 25 in ingress port, is linked with outlet port logical Toward the oil circuit of auxiliary adjustor 20g.The oil circuit towards fuel tank is linked with discharge port.
In addition, the cantilever being connected in the operating portion that valve 14c is controlled with cantilever third direction loads pilot line is provided with right The cantilever for being supplied loads the loading air relief valve 22b of cantilever 3 that pilot pressure oil is limited or disconnected.The cantilever 3 is loaded and is subtracted Pressure valve 22b passes through guide's hydraulic-driven.Air relief valve 22b is loaded to the cantilever 3 via the second switching valve 24 from guide's hydraulic power source 25 Supply pilot pressure oil.Correspondingly, cantilever 3 loads air relief valve 22b for supply with the pressure oil that air relief valve 22b is loaded to cantilever 3 Expand the connection area of the 3rd hydraulic pump 20c and fuel tank.
Second switching valve 24 is the pressure oil of the bottom side grease chamber to operating portion importing boom cylinder 7 and possesses spring in one side The switching valve that three port two position is put, has been linked with the oil circuit from guide's hydraulic power source 25 in ingress port, is linked with outlet port logical The oil circuit of the operating portion of air relief valve 22b is loaded toward cantilever 3.The oil circuit towards fuel tank is connected with discharge port.
Additionally, in the first switching valve 23 and the second switching valve 24, it is desirable to the boom cylinder 7 for being directed to operating portion The pressure of the pressure oil of bottom side grease chamber increases, in the way of 23 to the second switching valve 24 of the first switching valve first carries out switching action, The characteristic of each switching valve is adjusted.
In addition, in the present embodiment, it is also possible to be configured at the directional control valve of each pump line line 21a, 21b, 21c to driving The maximum of operated pilot pressure detected, and based on the detected value driving adjustor 20d, 20e, 20f.
According to the second embodiment of the hydraulic control device of the Work machine of the above-mentioned present invention, can obtain and first Embodiment identical effect.
In addition, the present invention is not limited to first, second above-mentioned embodiment, comprising various variations.It is above-mentioned Embodiment be to illustrate the present invention and be described in detail in order to easy to understand, be not limited to possess illustrated Entire infrastructure.For example, a part for the structure of certain embodiment can be replaced into the structure of other embodiment, in addition, Also the structure of other embodiment can be added in the structure of certain embodiment.In addition, it is also possible to the knot to each embodiment A part for structure carries out adding, eliminate, replacing for other structures.
The explanation of symbol
1-lower traveling body, 2-upper rotation, 2A-electromotor, 3-crane arm, 4-cantilever, 5-scraper bowl, 6- Crane arm cylinder, 7-boom cylinder (the first hydraulic unit driver), 8-scraper bowl cylinder, 9-action bars (operating portion), 10-control valve, 11-rotary fluid motor, 13a-crane arm first direction control valve, and 13b-crane arm controls valve with second direction, 14a-cantilever second direction controls valve, and 14b-cantilever first direction controls valve, and 14c-cantilever controls valve with third direction (the first control valve), 15a-scraper bowl directional control valve, 16c-revolution directional control valve, 20-hydraulic pumping unit, 20a- First hydraulic pump, 20b-the second hydraulic pump (the second hydraulic pump), the hydraulic pumps of 20c-the 3rd (the first hydraulic pump), 20d-the first Hydraulic pump adjustor, 20e-the second hydraulic pump adjustor, the hydraulic pump adjustors of 20f-the 3rd, 21a-the first pump line Line, 21b-the second pump line line, the pump line lines of 21c-the 3rd, 22-cantilever 3 load air relief valve (the first control valve), 22b-cantilever 3 Loading air relief valve (the first control valve), the 23-the first switching valve, the 24-the second switching valve, 100-controller, 101～108-first Pilot force transducer, 110-target action operational part, 120-connection control unit (control valve drive division), 130-flow-control Portion (flow-control portion), A7-crane arm cylinder bottom side grease chamber pressure transducer (load detecting portion).

Claims (5)

1. a kind of hydraulic control device of Work machine, possesses：
First hydraulic unit driver；The first hydraulic pump that can be connected with above-mentioned first hydraulic unit driver and the second hydraulic pump；Can Make first control valve of the pressure oil that above-mentioned first hydraulic pump is discharged to fuel tank circulation；And to above-mentioned first hydraulic unit driver The load detecting portion detected by load,
The hydraulic control device of above-mentioned Work machine is characterised by possessing：
Control valve drive division, the detection signal that its above-mentioned load detecting portion of reading detects, and according to above-mentioned first hydraulic-driven The increase of the load of device, to make above-mentioned first hydraulic pump control to above-mentioned first with connecting in the way of area expands for above-mentioned fuel tank Valve is driven；And
Flow-control portion, which is being pressed from above-mentioned first hydraulic pump and above-mentioned second hydraulic pump to the supply of above-mentioned first hydraulic unit driver In the case of power oil, the detection signal that above-mentioned load detecting portion detects is read in, and according to the negative of above-mentioned first hydraulic unit driver The increase of load, the control of the delivery flow for carrying out reducing above-mentioned first hydraulic pump.
2. the hydraulic control device of Work machine according to claim 1, it is characterised in that
In above-mentioned control valve drive division according to the increase of the load of above-mentioned first hydraulic unit driver so that above-mentioned first hydraulic pump with Before the mode that the connection area of above-mentioned fuel tank expands is driven to the above-mentioned first control valve, above-mentioned flow-control portion is according to upper The increase of the load of the first hydraulic unit driver is stated, the control of the delivery flow for carrying out reducing above-mentioned first hydraulic pump.
3. the hydraulic control device of Work machine according to claim 1, it is characterised in that
Above-mentioned flow-control portion can also carry out reduction control to the delivery flow of above-mentioned second hydraulic pump,
In the increase of the load according to above-mentioned first hydraulic unit driver, the control of the delivery flow for carrying out reducing above-mentioned second hydraulic pump Before system, the control of the delivery flow for carrying out reducing above-mentioned first hydraulic pump.
4. the hydraulic control device of Work machine according to claim 1, it is characterised in that
Possess：The first operating portion that action to above-mentioned first hydraulic unit driver is indicated；And to above-mentioned first operating portion The operational ton test section that detected of operational ton,
The detection signal that aforesaid operations amount test section is detected is read in above-mentioned flow-control portion, according to above-mentioned first operating portion The increase of operational ton, makes from above-mentioned first hydraulic pump the flow of the pressure oil supplied to above-mentioned first hydraulic unit driver increase it Before, increase from above-mentioned second hydraulic pump the flow of the pressure oil supplied to above-mentioned first hydraulic unit driver.
5. the hydraulic control device of Work machine according to claim 1, it is characterised in that
The delivery flow that above-mentioned first hydraulic pump after reduction is controlled is carried out by above-mentioned flow-control portion is above-mentioned first hydraulic pressure The standby flow of pump.
CN201580044422.1A 2014-11-06 2015-08-28 The hydraulic control device of Work machine Active CN106574641B (en)

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WO2016072135A1 (en) 2016-05-12
CN106574641B (en) 2018-06-29
EP3217019B1 (en) 2021-06-16
KR101894978B1 (en) 2018-09-04
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EP3217019A4 (en) 2018-08-22
KR20170031240A (en) 2017-03-20

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